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EP1091145B1 - Planeten-Reibradgetriebe - Google Patents

Planeten-Reibradgetriebe Download PDF

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Publication number
EP1091145B1
EP1091145B1 EP00121685A EP00121685A EP1091145B1 EP 1091145 B1 EP1091145 B1 EP 1091145B1 EP 00121685 A EP00121685 A EP 00121685A EP 00121685 A EP00121685 A EP 00121685A EP 1091145 B1 EP1091145 B1 EP 1091145B1
Authority
EP
European Patent Office
Prior art keywords
shaft
transmission member
coupling structure
ring roller
rotational
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00121685A
Other languages
English (en)
French (fr)
Other versions
EP1091145A2 (de
EP1091145A3 (de
Inventor
Kiyoji Minegishi
Jun Tamenaga
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sumitomo Heavy Industries Ltd
Original Assignee
Sumitomo Heavy Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sumitomo Heavy Industries Ltd filed Critical Sumitomo Heavy Industries Ltd
Publication of EP1091145A2 publication Critical patent/EP1091145A2/de
Publication of EP1091145A3 publication Critical patent/EP1091145A3/de
Application granted granted Critical
Publication of EP1091145B1 publication Critical patent/EP1091145B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H13/00—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members
    • F16H13/06—Gearing for conveying rotary motion with constant gear ratio by friction between rotary members with members having orbital motion

Definitions

  • the invention relates to a shaft coupling structure for coupling two rotating shafts coaxially opposed to each other to transmit rotational power from one of the rotating shafts to the other.
  • a rotating shaft for power transmission sometimes cannot be made long because of material measurements, overhauls, and the like. In such cases, shaft division is required, and a shaft coupling is widely used as a machine element for coupling the two shafts divided.
  • Fig. 9 shows a shaft coupling structure 1 in wide use heretofore.
  • a first shaft 2 and a second shaft 4 for rotational power transmission are coaxially opposed to each other.
  • the rotational power transmission between the first shaft 2 and the second shaft 4 is effected by a column-like member 8 having a shaft insertion hole 6 formed inside, to which the first shaft 2 and the second shaft 4 are inserted at the vicinities of their shaft ends.
  • the shaft insertion hole 6 is formed through the interior of the column-like member 8, and hence the column-like member 8 actually has the shape of a cylinder.
  • This shaft insertion hole 6 has a key slot 10 formed therein.
  • the first shaft 2 and the second shaft 4 each are provided with a key slot 12. Accordingly, the first and second shafts 2 and 4 are individually engaged with the column-like member 8 in the direction of rotation via driving keys 14.
  • safety covers 16 of short cylindrical shape are mounted on both sides of the column-like member 8 so that the heads of the driving keys 14 are prevented from exposure to exterior.
  • the first shaft 2 and the second shaft 4 are coupled to each other in the direction of rotation via the column-like member 8. Therefore, for example, rotational power input to the first shaft 2 is transmitted through the driving keys 14 and the column-like member 8 to the second shaft 4 with the same rotational speed.
  • This shaft coupling structure 20 is of flange type.
  • a first shaft 2 and a second shaft 4 are coaxially opposed to each other.
  • the rotational power transmission between the first shaft 2 and the second shaft 4 is effected by a first column-like member 22 having a shaft insertion hole 23 formed inside, to which the first shaft 2 is inserted at the vicinity of its shaft end, and a second column-like member 24 having a shaft insertion hole 25 formed inside, to which the second shaft 4 is inserted at the vicinity of its shaft end.
  • first and second column-like members 22 and 24 have a first flange portion 22A and a second flange portion 24A, both spreading radially outward, formed integrally on their opposing sides (the shaft-end sides of the first and second shafts 2 and 4), respectively.
  • Each of the flange portions 22A and 24A has a plurality of bolt holes 26 formed therethrough along the direction of the center axis L, at regular intervals along the circumferential direction.
  • the first shaft 2 and the shaft insertion hole 23 in the first column-like member 22 are provided with key slots 10 and 12, respectively, so that they are engaged with each other in the direction of rotation via a parallel key 28.
  • the second shaft 4 and the second column-like member 24 are in the same relationship.
  • the first flange portion 22A and the second flange portion 24A are coupled to each other by bolts 30 inserted through the bolt holes 26 and nuts 32 threadedly engaged with the bolts 30, so that the flange portions 22A and 24A make integral rotation.
  • rotational power input to the first shaft 2 is transmitted through the parallel key 28, the first column-like member 22, the bolts 30 and nuts 32, the second flange portion 24A, and the parallel key 28 in this order, to the second shaft 4 with the same rotational speed.
  • first column-like member 22 and the second column-like member 24 are substantially in an integral structure due to the bolts 30 and the nuts 32, much the same as the shaft coupling structure 1 shown in Fig. 9.
  • this shaft coupling structure 20 of flange type is particularly convenient when the first shaft 2 and the second shaft 4 have different shaft diameters, since the first column-like member 22 and the second column-like member 24 can be made of different members.
  • a rotary-machine driving apparatus 34 shown in Fig. 11 comprises a motor 36 having a motor shaft 36A, a speed reducer 42 having an input shaft 38 and an output shaft 40 in parallel, and a joint casing 44 for combining the motor 36 and the speed reducer 42 integrally.
  • the same shaft coupling structure 1 as that shown in Fig. 9 is used to couple the motor shaft 36A and the input shaft 38 to each other.
  • the first shaft 2 corresponds to the motor shaft 36A, and the second shaft 4 to the input shaft 38.
  • Rotational power from the motor shaft 36A is thus transmitted through this shaft coupling structure 1 to the input shaft 38 with the same rotational speed.
  • the role of the joint casing 44 is to couple the motor 36 and the speed reducer 42 integrally so as not to make relative rotations.
  • the joint casing 44 typically uses a circular cylindrical or square cylindrical member.
  • this driving apparatus 34 has a structure of mounting the motor 36 directly onto the speed reducer 42 via the joint casing 44, the motor 36 and the speed reducer 42 may be separately fixed to an independent motor base, speed-reducer base, and the like. In such a case, a safety cover and the like may be installed to prevent the shaft coupling structure 1 from exposure.
  • a shaft coupling structure sometimes functions to avoid a breakage of apparatuses to be connected.
  • the rotation of the speed reducer 42 in Fig. 11 is suddenly locked in an accident. Even so, the column-like member 8, the driving keys 14, or other components in the shaft coupling structure 1 can break down first to avoid an overload on the motor 36 and the like.
  • the motor 36, the speed reducer 42, and other apparatuses having rotating shafts has certain dimensions while the shaft coupling structure 1 for coupling the rotating shafts has highly compact configuration. That is, the space between the apparatuses arranged on both sides of the shaft coupling structure 1 actually has had no particular uses beneficial, other than to arrange a simple joint casing 44 or to install a safety cover over the shaft coupling structure 1 at best.
  • US-A1-4 648 288 which constitutes the closest prior art, discloses a planetary roller type power transmission device which has a first rotary shaft and a second rotary shaft which are arranged coaxially, a sun roller connected to the first rotary shaft, a stationary outer ring disposed concentrically with the sun roller, and a plurality of planet rollers disposed in the annular space between the sun roller and the stationary outer ring, the planet rollers being carried by a carrier rotatable as a unit with the second rotary shaft.
  • the power transmission device further has a pair of mutually opposing flange-like projections formed on the outer peripheral surface of the stationary outer ring so as to pass positions adjacent to respective axial ends of the area of contact between the planet rollers and the stationary outer ring, and a tightening means operable from the outside of the transmission device and adapted to urge the flange-like projections towards each other thereby causing elastic deformation of the stationary outer ring.
  • the present invention has been achieved in view of the foregoing problems. It is thus an object of the present invention to provide a shaft coupling structure which maintains and exerts the functions inherent to a shaft coupling structure as well as utilizes the empty space around the to-be-coupled two shafts for an additional speed change function.
  • a column-like member (as shown in Figs. 9 and 10) is divided into a first-shaft-2 side and a second-shaft-4 side to form a first transmission member A and a second transmission member B for making integral rotations with the shafts (the first shaft 2 and the second shaft 4), respectively.
  • a plurality of planetary rollers C are arranged around the first transmission member A so as to make rolling contact with the outer periphery A1 of the first transmission member A.
  • a ring roller D with the inner periphery D1 of which the plurality of planetary rollers C make rolling contact is arranged so as to be restrained on rotation by an external non-rotational member F.
  • each of the plurality of planetary rollers C is rotatably supported by a second transmission member B.
  • the second transmission member B can make rotation integral with the revolution of the planetary rollers C around the first transmission member A.
  • the first transmission member A and the second transmission member B can be regarded as a sun roller and a carrier, respectively, which means that this shaft coupling structure also serves as a simple planetary roller mechanism using frictional rollers. Accordingly, given that the first transmission member A makes the input element of rotational power, the shaft coupling structure functions as a reduction mechanism with the second transmission member B as the output element. When the second transmission member B makes the input element of rotational power, the shaft coupling structure functions as a step-up mechanism with the first transmission member A as the output element.
  • both the first transmission member A and the second transmission member B have a shaft insertion hole formed therein, and the first transmission member A and the second transmission member B are arranged on the same axis. This preserves the shaft coupling's essential function of "coupling the coaxially-opposed first and second shafts 2 and 4 to transmit rotational power.”
  • the rotational power is transmitted through the contact surfaces of the frictional rollers, i.e., of the planetary rollers C and the ring roller D. Therefore, the transmission produces no particularly high noise, preserving the property of "quietness" required of a shaft coupling.
  • this shaft coupling structure with speed change function is configured so that the contact surfaces of the rollers make a slip when subjected to rotational torque above a predetermined value. Therefore, even if an overload suddenly occurs on one of the rotating shafts, a breakage of the apparatus connected to the other rotating shaft can be avoided to a certain extent.
  • this shaft coupling structure also offers the function of "safety" required of a shaft coupling.
  • This shaft coupling structure with speed change function is somewhat greater in radial dimension due to the presence of the planetary rollers C and the ring roller D. This, however, means utilization of the space around a shaft coupling which has been wasted (not utilized) as stated before. Accordingly, the entire apparatus coupled will not be affected in size.
  • this shaft coupling structure with speed change function is provided with a high-ratio speed change function without losing the conventional shaft coupling functions. Therefore, when this shaft coupling structure is applied e.g. to couple a motor and speed change gears, it is possible to lower the gear ratio of the change gears to be coupled since the shaft coupling structure itself can achieve a certain change in speed. This makes the entire apparatus more compact.
  • the non-rotational member for restraining the rotation of the ring roller may come into engagement with and support the ring roller, and comprise a pair of flange portions spreading radially outward on the first and second transmission members, the flange portions being capable of establishing connection between a casing on the first-shaft side and a casing on the second-shaft side so that the rotation of the non-rotational member is restrained.
  • the easy coupling between the first-shaft side and the second-shaft side can extend to the casings.
  • the ring roller can be easily maintained in a non-rotational state.
  • Fig. 1 has shown, in functional terms, the ring roller D being engaged with an external non-rotational member for rotational restraint as fitted and fixed directly to the casing for accommodating this shaft structure.
  • the means for the rotational restraint is not limited thereto.
  • the ring roller D may be restrained on rotation by bolting, or by providing a projection on the ring roller D for engagement with the external non-rotational member. It is essential only that the rotation of the ring roller D be restrained in some way.
  • first and second transmission members A and B are not limited to certain specific configurations, and need not always have a column shape.
  • Fig. 3 is a partially sectional view of a geared motor 50 to which a shaft coupling structure with speed change mechanism according to a first embodiment is applied.
  • This geared motor 50 comprises: a motor unit 52 for generating rotational power; a reduction gear unit 54 containing an oscillating internal meshing gear reduction structure; and a coupling unit 56 for coupling this reduction gear unit 54 and the motor unit 52 to each other by using the shaft coupling structure according to the present invention.
  • the reduction gear unit 54 includes: an input shaft 58 to which rotational power is input; an external gear 60 supported by this input shaft 58 so as to be capable of eccentric oscillating rotations; an internal gear 62 which is integrally formed on a casing 66 and with which the external gear 60 makes internal mesh; and an output shaft 64 for extracting and transmitting only the rotational component of the external gear 60 which makes rotation and revolution while making internal mesh with the internal gear 62.
  • a motor shaft 52A (corresponding to the first shaft 2 in Fig. 1) and an input shaft 58 (corresponding to the second shaft 4 in Fig. 1) are coaxially opposed to each other.
  • the coupling unit 56 includes a first transmission member 68 for making integral rotation with the motor shaft 52A and a second transmission member 70 for making integral rotation with the input shaft 58.
  • Three planetary rollers 72 and a ring roller 76 are arranged around the first transmission member 68.
  • the planetary rollers 72 make rolling contact with the outer periphery of the first transmission member 68 and with the inner periphery of the ring roller 76.
  • the ring roller 76 is engaged with a casing (non-rotational member) 74 for rotational restraint.
  • the planetary rollers 72 are rotatably supported by the second transmission member 70.
  • the second transmission member 70 makes rotation integral with the revolution of the planetary rollers 72 around the first transmission member 68.
  • the first transmission member 68 is provided with a shaft insertion hole 58 to which the motor shaft 52A can be inserted.
  • the motor shaft 52A and the first transmission member 68 are engaged with each other in the direction of rotation by a key so as to make integral rotation.
  • the second transmission member 70 is provided with a shaft insertion hole 70B to which the input shaft 58 can be inserted.
  • the input shaft 58 and the second transmission member 70 are configured to make integral rotation via a spline connection.
  • each shaft insertion hole 68A in the first transmission member 68 and the shaft insertion hole 70B in the second transmission member 70 are formed through the respective transmission members 68 and 70, the present invention is not limited thereto.
  • each shaft insertion hole may be an "opening" that does not pass through completely.
  • the second transmission member 70 has three pins 70A extended in the direction of the center axis, at regular intervals along its circumferential direction. These pins 70A support the individual planetary rollers 72 rotatably.
  • the ring roller 76 has bolt holes 76A formed therein at regular intervals along its circumferential direction. The ring roller 76 is directly fixed to a projection 74A of the casing 74 by bolts 78 inserted through the bolt holes 76.
  • the reference numerals 80A and 80B represent planetary roller restraining members of ring shape, for restraining the axial movements of the planetary rollers 72.
  • one (80B) is coaxially fixed to an end face of the ring roller 76 by the bolts 78, and the other (80A) is arranged in a depression in the casing 74.
  • the casing (non-rotational member) 74 for accommodating the shaft coupling structure with speed change function has a pair of flanges 74B and 74C integrally formed thereon.
  • the flanges 74B and 74C spread radially outward at both sides of the first and second transmission members in the axial direction L.
  • One flange portion 74B is integrally coupled to a motor flange 52B of the motor unit 52.
  • the other flange portion 74C is integrally connected to the casing 66 of the reduction gear unit 54.
  • the coupling unit 56 is coupled to the motor unit 52 and the reduction gear unit 54 while achieving the restraint on the rotation of its ring roller 76.
  • the first transmission member 68 is rotatively driven by the motor shaft 52A.
  • the planetary rollers 72 interposed between the first transmission member 68 and the ring roller 76 make contact with the ring roller 76 for rotation while revolving around the first transmission member 68.
  • the second transmission member 70 rotatably supporting the planetary rollers 72 extracts only the revolution of the planetary rollers 72, and transmits this revolution to the input shaft 58.
  • this coupling unit 56 combines the shaft coupling's basic function of transmitting the rotational power of the motor shaft 52A to the input shaft 58 with the change gears' function of rotating the input shaft 58 with respect to the motor shaft 52A at a certain change gear ratio.
  • the reduction gear unit 54 to be coupled may be made more compact because some of its speed change function can be shared with the coupling unit 56.
  • the coupling unit 56 only utilizes the empty space (existing previously) between the reduction gear unit 54 and the motor unit 52, so that the entire geared motor 50 is hardly extended in the direction of the center axis L or enlarged in the radial direction.
  • the coupling unit 56 can well absorb vibrations caused by the oscillations of the external gear 60 in the reduction gear unit 54, vibrations from the motor unit 52, and the like far beyond general expectations. Although unknown in detail, the reason for this seems that the coupling unit 56 transmits rotational power by means of friction between the contact surfaces of the planetary rollers 72, the ring roller 76, and the first transmission member 68, and that it has a characteristic transmission mode of utilizing the rotation and revolution of the planetary rollers 72. Furthermore, even if impact torque is applied to either of the input shaft 58 and the motor shaft 52A, the impact torque is absorbed into a slip between the contact surfaces of the rollers. This allows the coupling unit 56 to relieve some of the impact which can be transmitted to the other shaft, thereby preventing a breakage of the reduction gear unit 54 and the motor unit 52.
  • a motor unit 92 and a reduction gear unit 94 are coupled to each other via a shaft coupling structure with speed change function.
  • a coupling unit 96 is interposed therebetween.
  • This coupling unit 96 is almost identical to the coupling unit 56 described in the first embodiment except in the means of fixing a ring roller 176, as shown in Fig. 7.
  • the ring roller 176 has an axial engage portion 98 projected radially outward from its outer periphery.
  • a casing 174 has a recess 100, capable of engagement with the engage portion 98, formed on its inner periphery along the axial direction. Then, this recess 100 and the engage portion 98 are brought into engagement to restrain the rotation of the ring roller 176.
  • planetary roller restraining members 180A and 180B for guiding planetary rollers 172 along the circumferential direction are coaxially fixed to both end faces of the ring roller 176 with bolts 178 and nuts 178A (see Fig. 6).
  • this coupling unit 96 is almost identical to that of the coupling unit 56 in the first embodiment. Therefore, identical or like parts will be designated by reference numerals having the same lower two digits as those employed in the coupling unit 56, and structural, functional, and other detailed descriptions thereof will be omitted.
  • the reduction gear unit 94 comprises: an input shaft 102 which is spline-connected to a second transmission member 170 at one end and has a hypoid pinion 102A integrally formed on the other end; a hypoid gear 104 meshing with the hypoid pinion 102A; a first pinion 106 for making coaxial, integral rotation with the hypoid gear 104; a first gear 108 meshing with the first pinion 106; a second pinion 110 for making coaxial, integral rotation with the first pinion 108; an output shaft gear 112 meshing with the second pinion 110; and an output shaft 114 of hollow type, piercing through the output shaft gear 112 at the center to support the output shaft gear 112.
  • rotational power from the motor unit 92 is transmitted through the coupling unit 96 to the input shaft 102 at a predetermined change gear ratio (reduction ratio).
  • the rotational power on the input shaft 102 is transmitted through the individual pinions and gears in the reduction gear unit 94 to the output shaft 114 having an orthogonal rotation axis, at a predetermined reduction ratio.
  • the means of fixing the ring roller 176 has a simple structure of engaging the casing recess 100 and the engage portion 98 of the ring roller 176 with each other. Therefore, just a little modification to a joint casing in a conventional use allows the diversion of the joint casing thereto.
  • the first and second embodiments described above have dealt only with the cases where the shaft coupling structure with speed change function in a coupling unit offers a speed reducing function with the first transmission member as the input element and the second transmission member as the output element.
  • the present invention is not limited thereto, and is also applicable to a speed increasing function with the second transmission member as the input element and the first transmission member as the output element.
  • both end faces of a casing 274 may be provided with (blind) bolt holes 274D instead of flanges.
  • the other configuration of the geared motor 250 is almost identical to that of the geared motor 50 shown in Fig. 3. Therefore, identical or like parts are designated by reference numerals having the same lower two digits as those employed in the geared motor 50, and structural, functional, and other detailed descriptions thereof will be omitted.
  • the above-described embodiments have dealt only with the cases where a coupling unit couples a motor unit and a reduction gear unit to each other. Nevertheless, the present invention is not limited thereto, and may be applied to every situation where coupling is established between two speed reducers, a speed reducer and a mating machine (any apparatus requiring rotational power), a motor and a mating machine, and the likes.
  • the means of fixing a ring roller are not limited to those mentioned in the above-described embodiments. It is essential only that any form of engagement be established with a member not making integral rotation with the rotating shafts (including the casing and others) for rotational restraint.
  • a shaft coupling structure can be obtained which is configured to maintain and exert the functions inherent to a shaft coupling structure, as well as to utilize the empty space around to-be-coupled two shafts for an additional speed change function.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Structure Of Transmissions (AREA)

Claims (4)

  1. Wellenkupplungsstruktur (56, 96, 256) zur Koppelung einer ersten Welle (52A, 252A) und einer zweiten Welle (58, 102, 258), die einander koaxial gegenüberstehen; wobei die Wellenkupplungsstruktur (56, 96, 256) eine Vielzahl von Planetenwalzen (72, 172, 272) und eine Hohlwalze (Hohllaufbahn) (76, 176, 276) aufweist, wobei die Vielzahl von Planetenwalzen (72, 172, 272) einen Wälzkontakt mit dem Innenumfang der Hohlwalze (76, 176, 276) herstellt, wobei die Hohlwalze (76, 176, 276) mit einem sich nicht drehenden Glied (74, 174, 274) zur Einschränkung in Drehrichtung in Eingriff ist;
    gekennzeichnet durch
    ein erstes Getriebeglied (68, 168, 268) auf einer Seite der ersten Welle und mit einem ersten Wellenloch (68A, 168A) zur Aufnahme der ersten Welle (52A, 252A);
    ein zweites Getriebeglied (70, 170, 270) auf einer Seite der zweiten Welle und mit einem zweiten Wellenloch (70B) zur Aufnahme der zweiten Welle (58, 102, 258),
    wobei die erste Welle (52A, 252A) und die zweite Welle (58, 102, 258) in das erste Wellenloch (68A, 168A) bzw. das zweite Wellenloch (70B) einzuführen sind, wobei die Drehleistungsübertragung zwischen der ersten Welle (52A, 252A) und der zweiten Welle (58, 102, 258) durch die ersten und zweiten Getriebeglieder bewirkt wird,
    wobei die Vielzahl von Planetenwalzen (72, 172, 272) und die Hohlwalze (76, 176, 276) um das erste Getriebeglied (68, 168, 268) herum angeordnet ist, und wobei die Vielzahl von Planetenwalzen (72, 172, 272) einen Wälzkontakt mit dem Außenumfang des ersten Getriebegliedes (68, 168, 268) und mit dem Innenumfang der Hohlwalze (76, 176, 276) herstellen; und
    wobei das zweite Getriebeglied (70, 170, 270) die Vielzahl von Planetenwalzen (72, 172, 272) drehbar so trägt, dass das zweite Getriebeglied (70, 170, 270) eine Drehung integral mit der Umdrehung der Vielzahl von Planetenwalzen (72, 172, 272) um das erste Getriebeglied (68, 168, 268) herum ausführt.
  2. Wellenkupplungsstruktur (56, 96, 256) nach Anspruch 1, wobei
    die erste Welle (52A, 252A) und die zweite Welle (58, 102, 258) durch ein Gehäuse der ersten Wellenseite bzw. ein Gehäuse der zweiten Wellenseite getragen werden; und
    wobei das sich nicht drehende Glied (74, 174, 274) eine Verbindung mit dem Gehäuse auf der ersten Wellenseite und/oder dem Gehäuse auf der zweiten Wellenseite einrichten kann, um festgelegt zu sein.
  3. Wellenkupplungsstruktur (56, 96, 256) nach Anspruch 2, wobei das sich nicht drehende Glied (74, 174, 274) den Außenumfang der Hohlwalze bzw. Hohllaufbahn (76, 176, 276) fest trägt und ein Paar von Flanschteilen (74A, 74B, 74C) aufweist, die sich radial nach außen an den ersten und zweiten Getriebegliedern ausbreiten, wobei die Flanschteile (74A, 74B, 74C) eine Verbindung zwischen dem Gehäuse auf der ersten Wellenseite und dem Gehäuse auf der zweiten Wellenseite einrichten können, so dass die Drehung des sich nicht drehenden Gliedes (74, 174, 274) eingeschränkt ist.
  4. Wellenkupplungsstruktur (56, 96, 256) nach einem der vorhergehenden Ansprüche, wobei
    die zweite Welle (58, 102, 258) eine Eingangswelle einer Reduktionsgetriebeeinheit ist, wobei die Eingangswelle eine Keilanordnung hat, wobei eine Gegenkeilanordnung in Eingriff mit der Keilanordnung der Eingangswelle in dem Loch (70B) für die zweite Welle des zweiten Getriebegliedes (70, 170, 270) ausgeformt ist, und
    wobei die Eingangswelle der Reduktionsgetriebeeinheit und des zweiten Getriebegliedes (70, 170, 270) durch die Keile verbunden sind.
EP00121685A 1999-10-04 2000-10-04 Planeten-Reibradgetriebe Expired - Lifetime EP1091145B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP28301599A JP2001108028A (ja) 1999-10-04 1999-10-04 変速機能付の軸継手構造
JP28301599 1999-10-04

Publications (3)

Publication Number Publication Date
EP1091145A2 EP1091145A2 (de) 2001-04-11
EP1091145A3 EP1091145A3 (de) 2003-06-11
EP1091145B1 true EP1091145B1 (de) 2006-12-20

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP00121685A Expired - Lifetime EP1091145B1 (de) 1999-10-04 2000-10-04 Planeten-Reibradgetriebe

Country Status (7)

Country Link
US (1) US6436000B1 (de)
EP (1) EP1091145B1 (de)
JP (1) JP2001108028A (de)
KR (1) KR100392697B1 (de)
CN (1) CN100374758C (de)
DE (1) DE60032431T2 (de)
TW (1) TW442620B (de)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7118512B2 (en) * 2000-09-08 2006-10-10 Iowa State University Research Foundation, Inc. Self-actuating, traction-drive speed changer
JP2007028883A (ja) * 2005-06-16 2007-02-01 Sumitomo Heavy Ind Ltd ギヤドモータ及びギヤドモータ用軸部材
US7513028B2 (en) * 2006-02-15 2009-04-07 General Electric Company Systems and methods for repairing a rotor system keyway
US20100031935A1 (en) * 2008-08-05 2010-02-11 Vandyne Ed Super-turbocharger having a high speed traction drive and a continuously variable transmission
JP2012225488A (ja) * 2011-04-22 2012-11-15 Toyota Industries Corp トルク伝達機構
CN102853059B (zh) * 2012-08-31 2016-06-01 广东明阳风电产业集团有限公司 一种风力发电机组齿轮箱试验台的旋转支撑组件
CN106051118A (zh) * 2016-06-17 2016-10-26 中国船舶重工集团公司第七�三研究所 同心传动结构
WO2019139158A1 (ja) * 2018-01-15 2019-07-18 満男 松岡 同速倍力装置
NO346168B1 (no) * 2019-06-26 2022-04-04 Svein Aaslund Transmisjon
CN112343932B (zh) * 2020-11-24 2022-06-03 浙江浙研冷挤压有限公司 一种基于不规则内圈的弹性联轴器

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1425760A1 (de) * 1962-01-05 1969-03-20 Demag Ag Membranabstuetzung fuer Planetengetriebe
US4483216A (en) * 1978-02-20 1984-11-20 Mitsubishi Jukogyo K.K. Planetary-roller transmission with elastic roller or ring
DE2935088C2 (de) * 1979-07-10 1983-10-27 Mitsubishi Jidosha Kogyo K.K., Tokyo Planetenreibungsgetriebe
JPS58113084A (ja) * 1981-12-28 1983-07-05 三菱電機株式会社 駆動装置
JPS6077841U (ja) * 1983-11-01 1985-05-30 株式会社三共製作所 遊星ロ−ラ式動力伝達装置
JPH04151053A (ja) * 1990-10-12 1992-05-25 Takashi Takahashi トラクション型変速装置
US5851163A (en) * 1996-03-29 1998-12-22 Ntn Corporation Planetary roller type power transmission device

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EP1091145A2 (de) 2001-04-11
DE60032431T2 (de) 2007-04-12
KR100392697B1 (ko) 2003-07-28
CN100374758C (zh) 2008-03-12
KR20010067284A (ko) 2001-07-12
DE60032431D1 (de) 2007-02-01
JP2001108028A (ja) 2001-04-20
TW442620B (en) 2001-06-23
CN1290823A (zh) 2001-04-11
EP1091145A3 (de) 2003-06-11
US6436000B1 (en) 2002-08-20

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